KR20070063443A - Differential gears - Google Patents

Abstract

A differential apparatus is provided to prevent generation of frictional noise of a clutch disk by supplying lubricating oil from a combination part between a side gear and a clutch disk from to a gap between sliding surfaces of clutch disks. A differential apparatus(10) includes a clutch unit(16) having a first clutch disk(12) and a second clutch disk(14). The first clutch disk is rotated by the side gear. The second clutch disk is rotated by a differential case(13). A lubricating oil supply unit(40) supplies lubricating oil from a combination part(17) between the side gear and the clutch disk to a gap between sliding surfaces of the first and second clutch disks.

Description

DIFFERENTIAL GEARS

1 is a cross-sectional view of a differential device.

Fig. 2 is a right side view of the side gear on the left side and a first clutch plate coupled thereto.

3 is a right side view of a side gear on the left side and a second clutch plate coupled thereto.

4 is a longitudinal sectional view of the left side gear.

5 is a right side view and (b) a left side view of the left side gear.

6 (a) and 6 (b) are explanatory diagrams of the operation of the operation means.

FIG. 7 is a diagram corresponding to FIG. 1 of a differential apparatus of another configuration. FIG.

8 is a cross-sectional view of a differential apparatus according to the prior art.

* Description of the symbols for the main parts of the drawings *

1 axle 2 drive shaft

3 drive pinion 10 differential

11 side gear

12 First clutch plate (板 pawl clutch 板)

12a Sliding surface 12b Inner pawl

13 differential gear case

14 2nd pawl clutch 板

14a Sliding surface 14b Outer pawl

15 pinion gear 16 clutch means

17 Joint 18 Pressure ring

18a outer pole 19 pinion shaft

19a shaft 20 clearance

21 Pressing means 22 Operating means

23 Cover member 24 Case body

25 Thread groove 26 Flange

27 Ring gear 28 Gear part

29 Rod member 30 Compression coil spring

31 Cam part 31a Operating surface

32 Cam groove 32a Inclined cam surface

33 Disc Spring 34 Spline Shaft

34a spline gear 40 lubricant supply

41 main road 42 guide home

43 Oil reservoir 44 Radial connection furnace

45 Oil supply groove 46 Oil storage hole

47 Cylindrical oil groove 50 Lubricant supply means

51 side gear 52a spline groove

52 Spline Shaft 53 Clutch Means

54 First clutch plate (內側 pawl clutch 板)

55 coupling

56 Oil reservoir 57 Through hole

58 2nd clutch plate

100 differential

101 Differential Gear Case 102 Axle

103 Pressure ring 104 Pinion shaft

105 pinion gear 106 side gear

107 Clearance 108 Control Means

109 Clutch means 110 Cam part

111 Cam groove 112 Elastic member

113 clutch plate

The present invention relates to a differential device having clutch means for differential restriction.

As a differential of a vehicle, for example, a limited slip differential gear having a differential limiting function such that sufficient torque is transmitted to the other wheel through the clutch means when only one wheel is about to idle. If one wheel is placed on ice, snow or sludge, it prevents the wheels from idling and does not transmit sufficient torque to the other wheels, or prevents the shaking of the body in turning or sudden starts It is widely adopted to.

For example, Patent Documents 1 and 2 describe a differential device 100 as shown in FIG. The differential device 100 comprises a pair of pressure rings 103 installed in the differential gear case 101 freely in the direction of the axle 102 and incapable of relative rotation, and the axle shaft having the shaft end supported therebetween. The pinion gear 105 is formed as a pinion shaft 104 orthogonal to the 102, a pinion gear 105 provided so as to be freely rotated on the pinion shaft 104, and a pair of side gears 106 provided so as not to rotate relative to the shaft ends of the left and right axles 102. A pair of side gears 106 inserted into and engaged with the pinion gears 105 on both sides thereof, and a pressure ring 103 according to an increase in the relative rotation torque between the pinion shaft 104 and the differential gear case 101 in the differential case. Operation means 108 for operating the pressure ring 103 in a direction in which the clearance 107 therebetween increases, and the axle direction of the pair of pressure rings 103 The clutch means 109 disposed on both sides is provided with a clutch means 109 which is operated by the pressure ring 103 and limits the differential of the left and right axles 102 as the clearance 107 increases.

Although various shapes are proposed as the operation means 108, for example, a quadrangular cam portion 110 having one diagonal line set in the axle direction is formed at the shaft end of the pinion shaft 104, and the pressure ring 103 is roughly coupled with the cam portion 110. A V-shaped cam groove 111 is adopted.

Further, in the differential device 100, a relative rotational torque is generated between the pinion shaft 104 and the differential gear case 101, and the clearance means 107 between the pressure rings 103 is widened by the operation means 108, so that the clutch means 109 operates so that the left and right wheel differentials are actuated. Although normally limited, an elastic member 112, such as a disc spring, is disposed outside the axle direction of both clutch means 109 so that the clearance 107 of both pressure rings 103 is returned to the set interval through the plurality of clutch plates 113 of the clutch means 109. The pressure ring 103 is configured to press in a direction approaching each other.

However, since the elastic member 112 of the differential device 100 presses the pressure ring 103 through the clutch plate 113 in a direction approaching each other, when the pressing force is set weakly, the clutch means 109 is easily operated by the operating means 108 and thus the low speed. Even in the case of turning, the differential limit is not stabilized. If the differential state is not stable, and the pressing force is increased, the operating means 108 becomes a differential state, but the clutch plate 113 always rubs due to the pressing force of the elastic member 112. Since it is press-contacted and becomes a substantially differential limiting state, eventually, the differential state in the case of turning at low speed cannot be secured stably. That is, when turning at a low speed, a small radius of rotation cannot be made, or a so-called chattering phenomenon occurs in which the differential limit state and the differential state are alternately generated, resulting in deterioration of the maneuverability or shock during chattering. There is a problem that adversely affects the differential device 100 and its peripheral devices.

For this reason, the present applicant has proposed and put into practical use a differential apparatus in Patent Document 3, in which a pressing means for pressing both pressure rings in a direction approaching each other without passing through the clutch plate is configured so that the differential state and the differential limit state are properly switched. Doing.

Patent Document 1: Japanese Patent Application Publication No. 55-27980

Patent Document 2: Japanese Patent Application Laid-Open No. 58-221046

Patent Document 3: Japanese Patent Application Laid-Open No. 2001-289305

However, in the inventions described in Patent Documents 1 and 2, in addition to the above problems, the clutch plate is always in sliding contact state by the elastic member, so that the friction sound is generated by sliding between the clutch plates when the clutch plate is in a differential state within the initial torque. There was a problem.

In addition, in the invention described in Patent Document 3, the frictional sound problem is greatly improved as compared with the differential devices described in Patent Documents 1 and 2, because the pressure rings are pushed in a direction approaching each other without passing through the clutch plate. Since the clutch plate is pressurized with the elastic member so that the clearance between the plates is reduced and the switching between the differential state and the differential limit state is facilitated, there remains a problem that a slight noise occurs.

An object of the present invention is to provide a differential device which can effectively prevent the friction sound of a clutch plate with a simple configuration.

The present applicant has found out that the cause of friction noise due to sliding between the clutch plates is that the lubricating oil is dropped from the sliding surface of the clutch plate, and the configuration of supplying the lubricating oil to the sliding surface of the clutch plate with a simple configuration is carefully examined. Thus, the present invention has been completed.

The differential device according to the present invention includes a first clutch plate integrally rotating with a side gear, and a second clutch plate integrally rotating with a differential gear case. A differential device comprising a clutch means comprising: a lubricating oil supply means for supplying lubricating oil in a differential gear case between a sliding surface of both clutch plates from a coupling portion of the side gear and the clutch plate; Is installed.

In the above differential device, the lubricating oil in the differential gear case is supplied by the lubricating oil supplying means from the engaging portion of the side gear and the clutch plate to the sliding surface of both clutch plates, thereby lubricating the sliding surface, so that the friction sound on the sliding surface of the clutch plate is lubricated. The occurrence of is effectively prevented.

Here, as a first embodiment of the lubricating oil supply means, a connection path connecting the toothed portion of the side gear and the engaging portion of the side gear and the clutch plate can be formed in the side gear. In the lubricating oil supply means of this first embodiment, the lubricating oil in the differential gear case engaged with the engaging portion of the side gear and the pinion gear is connected to the side gear and the clutch via a connection path connected to the base of the side gear by a pumping action at the engaging portion. It is conveyed to the engaging portion of the plate and supplied from the engaging portion between the sliding surfaces of both clutch plates, whereby the sliding surface is lubricated, so that the occurrence of friction noise on the sliding surface of the clutch plate is effectively prevented.

In addition, in the lubricating oil supply means of the first embodiment, an oil reservoir may be formed at a coupling portion of the side gear and the clutch plate, and a connection passage may be connected to the oil reservoir. In this case, lubricating oil can be equally supplied from the oil reservoir between the plurality of sliding surfaces. In addition, since the lubricating oil of the oil reservoir portion is about to move outward in the radial direction due to the centrifugal force by the rotation of the side gear, the lubricating oil can be more efficiently transferred between the two clutch plates.

In the lubricating oil supply means of the first embodiment, the oil storage portion may be formed in the differential gear case at an end portion on the side opposite to the gear portion of the side gear. As a differential device, a sliding contact of the side opposite to the gear part of the side gear with the differential gear case is widely adopted. In the differential device of this configuration, the oil storage part is differential at the end opposite to the gear part of the side gear. If it is formed in the gear case, the lubricating oil can be supplied to the sliding contact portion of the side gear and the differential gear case, and it is preferable because seizure of the sliding contact portion can be prevented.

As a second embodiment of the lubricating oil supply means, an oil storage portion may be formed at the engaging portion of the side gear and the clutch plate, and the end of the oil storage portion may be connected to the differential gear case on the side opposite to the gear portion of the side gear. In the lubricating oil supply means of this second embodiment, the lubricating oil in the differential gear case flowing into the oil storage portion formed in the engagement portion of the side gear and the clutch plate rotates together with the side gears, so that both of the clutch plates are removed from the oil storage portion by centrifugal force. It is conveyed between the sliding surfaces, whereby the sliding surfaces are lubricated so that the generation of friction noises on the sliding surfaces of the clutch plate is effectively prevented.

In the lubricating oil supply means of the first and second embodiments, the oil storage portion may form an oil storage portion by omitting a portion of at least one coupling portion of the side gear and the first clutch plate.

As an embodiment of the clutch plate in the differential device, lubricant oil supplied to the engaging portion of the side gear and the clutch plate is supplied to at least one of the first clutch plate and the second clutch plate between the sliding surfaces of both clutch plates. To form an oil supply groove. By forming such an oil supply groove, the lubricating oil supplied to the engaging portion can be smoothly supplied between the sliding surfaces of both clutch plates.

In the clutch plate of the above embodiment, it is a preferred embodiment to form an annular oil groove connected to an oil supply groove on at least one sliding surface of the first clutch plate and the outer clutch plate. In this configuration, the entire circumference of the sliding surface can be uniformly lubricated by the lubricating oil supplied from the oil supply groove to the annular oil groove, and the friction sound of the clutch plate can be further reduced. The oil supply groove and the annular oil groove are preferably arranged such that lubricating oil is supplied between each sliding surface of the adjacent clutch plate. The oil supply groove and the annular oil groove may be formed on both surfaces of one or both clutch plates of the first clutch plate and the second clutch plate, but the first clutch plate and the second clutch do not deteriorate as much as possible. It is desirable to engage both clutch plates so that they are formed on one side of the plate and the oil supply groove and the annular oil groove are arranged on each of the sliding surfaces.

In the clutch plate of the above embodiment, it is also a preferred embodiment to form an oil storage hole for storing lubricating oil supplied from an oil supply groove in at least one sliding surface of the first clutch plate and the second clutch plate. In such a case, excess lubricant can be stored in the oil storage hole when there is sufficient lubricant on the sliding surface, and lubricant can be supplied from the oil storage hole to the sliding surface when the lubricant is insufficient. Can be. In addition, since the lubricating oil can be supplied to the sliding surface facing the opening of the oil storage hole in an area, the lubricating oil can be supplied to the sliding surface entirely by setting the opening area of the oil storage hole large. have. Particularly, if the oil storage holes are formed in both the first clutch plate and the second clutch plate, it is possible to allow the lubricating oil to pass in and out between the oil storage holes of both clutch plates, so that the plurality of sliding surfaces can be lubricated equally. Do.

It is also a preferred embodiment to form a plurality of the oil storage holes at predetermined intervals in the circumferential direction of the clutch plate, and to change the radial position of the clutch plate in the adjacent oil storage holes. In this way, the lubricating oil can be supplied to the entire sliding surface while reducing the opening area of the oil storage hole and preventing the reduction in the strength and rigidity of the clutch plate.

(Example)

Best Mode for Carrying Out the Invention Embodiments of the present invention will be described below with reference to the drawings.

As shown in Figs. 1 to 4, the differential device 10 includes a first clutch plate 12 which rotates integrally with the side gear 11 and a second clutch plate 14 which rotates integrally with the differential gear case 13. As a differential device 10 having means 16, lubricant supply means 40 for supplying lubricating oil in the differential gear case 13 from the engagement portion 17 of the side gear 11 and the clutch plates 12, 14 between the sliding surfaces 12a, 14a of both clutch plates 12, 14. Is installed. However, the present invention can be applied to a differential device of any configuration as long as the pinion gear 15 and the side gear 11 for differential and the clutch means 16 for differential restriction are provided.

The differential device 10 includes a differential gear case 13 which rotates by a driving force from the engine with the left and right axles 1 as the center of rotation, and a left and right 1 which are respectively provided so that relative rotation is impossible at the shaft ends of the left and right axles 1 in the differential gear case 13. Between the pair of side gears 11 and the left and right side gears 11 at a small distance from the outside, the pair of left and right pressure rings 18 rotating integrally with the differential gear case 13 and between the left and right pressure rings 18 The pinion shaft 19 supported at the shaft end and orthogonal to the axle 1, the pinion gear 15 mounted freely on the shaft portion 19a of the pinion shaft 19 and engaged with the left and right side gears 11, and the axle shafts of both pressure rings 18. It is installed between the side wall portion of the differential gear case 13 and the side gear 11 on both sides in the opposite direction, and alternates along the axle direction. A pair of clutch means 16 including a first clutch plate 12 and a second clutch plate 14 arranged in the first position; and pressurizing means 21 for pressurizing both pressure rings 18 in a direction in which clearance 20 between both pressure rings 18 is narrowed. When the relative rotation torque between the pinion shaft 19 and the differential gear case 13 increases during differential operation, the pressure ring 18 is resisted against the pressing force of the pressing means 21 in a direction in which the clearance 20 between both pressure rings 18 increases. Operation means 22 for operating the clutch means 16 and lubricating oil supply means 40 for supplying lubricating oil in the differential gear case 13 between the sliding surfaces 12a, 14a of both clutch plates 12, 14.

The differential gear case 13 is formed by dividing the cover member 23 and the case main body 24, and a plurality of screw grooves 25 extending in the axle direction over its entire length are set in the circumferential direction on the inner circumferential surface of the case main body 24. It is formed at intervals, and the lid member 23 is fixed to a flange portion 26 formed at the left end of the case main body 24. A ring gear 27 is fixed to the flange portion 26, and the ring gear 27 is coupled to the drive pinion 3 provided on the drive shaft 2 of the engine. In the differential gear case 13, the shaft ends of the left and right axles 1 are inserted in the shape of the same shaft through the right wall of the cover member 23 and the case main body 24. The differential gear case 13 includes the drive pinion 3 and the ring gear 27. It is configured to rotate with the axle 1 as the rotation center by the driving force from the engine.

In the differential gear case 13, side gears 11 are not provided at the shaft ends of the left and right axles 1 so that relative rotation is impossible, and the left and right side gears 11 have a pair of left and right pressure rings 18 at a slight distance from the outside. The outer circumferential portion of both of the pressure rings 18 is formed in an engaging form, and an outer pawl portion 18a is formed on the outer circumferential portion of both pressure rings 18 so as to engage the screw groove 25 of the case body 24. It is free to move and relative rotation is impossible.

A cross-shaped pinion shaft 19 having four shaft portions 19a extending perpendicular to the axle 1 is provided between the side gears 11, and the four middle portions of each shaft portion 19a engage with the left and right side gears 11. Pinion gears 15 are installed so as to rotate freely. The number of pinion gears 15 can be set arbitrarily, but at least one pair is provided.

As shown in Figs. 1 and 6, the left and right pressure rings 18 are urged in a direction always approached by the pressing means 21 composed of a rod member 29 and a compression coil spring 30. As shown in Figs. A cam portion 31 is formed on the outer end of the shaft portion 19a of the pinion shaft 19, and a cam groove 32 for supporting the cam portion 31 from both sides is formed on the opposite surface of the outer peripheral portion of the pressure ring 18, and the cam portion 31 is formed. And the cam groove 32 constitute an operation means 22. The pinion shaft 19 is configured to rotate integrally with the differential gear case 13 and the pressure ring 18 by the cam portion 31 being supported by the cam groove 32 of the left and right pressure rings 18. On the other hand, the shapes of the cam portion 31 and the cam groove 32 of the operation means 22 may adopt known shapes other than those shown in the drawings. As the pressurizing means 21, any structure can be adopted as long as it can pressurize the pressure rings 18 in a direction approaching each other. Reference numeral 33 is a disc spring provided for the purpose of eliminating the gap between the clutch plates 12 and 14, and may be omitted if it is possible to assemble the clutch means 16 with substantially no play.

As shown in Figs. 1 to 3, the clutch means 16 is provided between the side wall portion of the differential gear case 13 and the side gear 11 on both sides of the axle direction of both pressure rings 18, and alternately arranged along the axle direction. One clutch plate 12 and a second clutch plate 14 are provided. On the outer circumferential portion of the second clutch plate 14, an outer pole portion 14b engaging with the screw groove 25 of the differential gear case 13 is formed to protrude outward, so that the second clutch plate 14 is moved in the axle direction with respect to the differential gear case 13. It is assembled freely and without relative rotation. The spline shaft part 34 is formed in the outer peripheral part of the side gear 11 over the full length, and the inner pole part 12b which engages with the spline shaft part 34 in the inner peripheral part of the 1st clutch plate 12 is located in an inward direction. Formed in a protruding shape, the first clutch plate 12 is coupled to the side gear 11 freely in the axle direction and incapable of relative rotation.

In the differential device 10, when the drive shaft 2 of the engine rotates, the pressure ring 18 and the pinion shaft 19 rotate together with the differential gear case 13 through the drive pinion 3 and the ring gear 27 as shown in FIG. When the rotational resistances of the left and right wheels are the same, the pinion gear 15 does not rotate around the shaft portion 19a but only rotates around the axle with the side gear 11 so that the left and right wheels rotate at the same speed. When the rotational resistance of one of the wheels decreases, the pinion gear 15 is engaged with the side gear 11 by a part of the rotational force acting on the differential gear case 13, so that the wheels on the side with the low rotational resistance rotate around the axle. The rotational speed becomes faster than the wheel on the larger side, but at high speeds and high loads, the cam portion 31 and the cam groove 32 of the operating means 22 rotate relatively little to resist the pressing force of the pressing means 21. The clearance 20 of the pressure ring 18 is adjusted so that the relative rotation of the side gear 11 and the differential gear case 13 is in a differential limit state in which the clutch plate 12 and 14 of the clutch means 16 are limited by frictional pressure forces. Improved maneuverability at high speeds and high loads while improving turnability at low speeds do.

More specifically, when a difference in rotational resistance occurs between the left and right wheels during the forward driving, the relative rotation torque P is generated between the pinion shaft 19 and the differential gear case 13 as shown in FIG. Due to the relative rotation torque P, the operating force F acts on both pressure rings 18 in a direction away from each other via the operating surface 31a of the cam portion 31 and the inclined cam surface 32a of the cam groove 32, as shown in Fig. 6 (b). As described above, the pinion shaft 19 and the differential gear case 13 are relatively minutely rotated so that the contact position between the operating surface 31a of the cam portion 31 and the inclined cam surface 32a of the cam groove 32 is about to increase the clearance 20. On the other hand, since the pressing force which tries to approach each other by the pressurizing means 21 always acts on both pressure rings 18, when the operating force F of the operating means 22 is smaller than the pressing force of the pressurizing means 21, the minimum clearance as shown in FIG. When 20 is maintained and becomes a differential state, and the operating force F becomes larger than the pressing force, as shown in Fig. 6 (b), the clearance 20 increases according to the force difference, and the clutch plates 12, 14 It is pressurized and friction-welded between the clutch plates 12 and 14, and it becomes a differential limit state.

The present invention is to prevent the occurrence of friction noise due to sliding between the clutch plates 12 and 14 when the differential device 10 is in a differential state within the initial torque, and the coupling portion of the side gear 11 and the clutch plates 12 and 14 is prevented. Lubricant supply means 40 for forcibly supplying the lubricating oil in the differential gear case 13 is provided between the sliding surfaces 12a and 14a of both clutch plates 12 and 14 from 17. FIG.

Referring to the lubricating oil supply means 40, as shown in Figs. 1 to 5, four main connecting passages 41 extending in the axial direction are formed at regular intervals in the circumferential direction in the radially middle portion of the side gear 11. One end of the main connection path 41 is connected toward the side wall of the differential gear case 13, and the other end is connected to the bottom of the gear portion 28 of the side gear 11. A guide groove 42 extending in the radial direction is formed at an end portion of the side gear 11 at the side wall side of the differential gear case 13, and an inner circumferential side end portion of the guide groove 42 is connected to one end of the main connection passage 41. The number of main connection passages 41 can be set arbitrarily. In addition, one end of the side wall of the differential gear case 13 in the main connection path 41 may be closed so that the pressure in the main connection path 41 does not decrease.

The number of teeth of the spline gear 34a of the spline shaft portion 34 is set to an even multiple of the number of teeth of the side gear 11, and at a circumferential position corresponding to the main connection path 41 and at least in the outer engagement region of the clutch plates 12, 14. The spline gear 34a has its entirety or a radial outer end thereof missing, and an oil reservoir 43 extending in the axial direction is formed between the portion where the spline gear 34a is missing and the first clutch plate 12. On the outer circumferential portion of the side gear 11, a pair of radial connection paths 44 are formed, one end of which is connected to the middle part of the main connection path 41 and the other end of which is connected to the oil reservoir 43.

Meanwhile, the number of radial connection paths 44 to one main connection path 41 can be arbitrarily set. It is also possible to form a slit-shaped radial connection path extending in the axial direction or the circumferential direction instead of the through-hole radial connection path 44. The main connection path 41 and the radial connection path 44 corresponds to the connection path. The oil reservoir 43 is preferably provided so as to constantly supply lubricant oil to the sliding surfaces 12a, 14a of the plurality of clutch plates 12, 14, but may be omitted. In addition, although the oil storage part 43 was formed by missing the spline gear 34a, it is also possible to form the oil storage part 43 by missing all or the inner peripheral part of the inner pole part 12b of the 1st clutch board 12 corresponding to the main connection path 41. As shown in FIG. The oil reservoir 43 may be formed by forming the spline groove of the spline shaft portion 34 corresponding to the main connection path 41 into a groove deeper than the other grooves. In addition, in order to connect the radial connection 44 to the oil reservoir 43 formed by missing the spline gear 34a, the number of teeth of the spline gear 34a was set to an even multiple of the number of teeth of the side gear 11, but the inner pole 12b was missing. When the oil reservoir is formed, the number of teeth of the spline gear 34a is set to an odd multiple of the number of teeth of the side gear 11. However, it is also within the scope of the present invention to set the number of teeth of the spline gear 34a irrespective of the number of teeth of the side gear 11.

A plurality of oil storage holes 46 are formed in the radially middle portion of the first clutch plate 12 and the second clutch plate 14 at predetermined intervals in the circumferential direction, and the plurality of oil storage holes 46 are formed in adjacent oil storage holes 46. It is formed while changing the radial position in this, and it is comprised so that the 1st clutch board 12 and the 2nd clutch board 14 may rotate about the whole of sliding surface 12a, 14a by relative rotation. In addition, the oil storage holes 46 of the first clutch plate 12 and the second clutch plate 14 are formed at the same position so that the lubricating oil in the oil storage hole 46 can enter and exit between the two clutch plates 12 and 14, and the oil storage holes 46 are stored in the oil storage hole 46. It is comprised so that lubricating oil to become constant may be.

An oil supply groove 45 and an annular oil groove 47 are formed in one sliding surface 12a of the first clutch plate 12 and one sliding surface 14a of the second clutch plate 14, respectively. The oil supply groove 45 is radially formed on the sliding surfaces 12a and 14a, the inner circumferential side end of the oil supply groove 45 is connected to the oil reservoir 43, and the outer circumferential end of the oil supply groove 45 is connected to every other oil storage hole 46. It is. The annular oil groove 47 is formed in the radially middle portion of the sliding surfaces 12a and 14a, and the adjacent oil storage holes 46 are connected by the annular oil groove 47.

On the other hand, the number of the oil supply groove 45 and the oil storage hole 46 can be arbitrarily set in accordance with the number of the oil storage portion 43. In addition, although adjacent oil storage holes 46 are preferably configured to have different radial positions, it is also possible to form the same radial positions. The shape of the oil storage hole 46 is formed as a round hole, but it is also possible to form the shape of an elongated oval or a long hole in the radial direction. The cyclic oil groove 47 may be formed in a plurality of concentric shapes, or may be formed in a wave shape such as a sine wave. The oil supply groove 45 and the annular oil groove 47 may be formed on both surfaces of one of the first clutch plate 12 and the second clutch plate 13, or may be formed on both surfaces of both. If lubricating oil can be sufficiently supplied to the sliding surfaces 12a and 14a of both clutch plates 12 and 14, one of the oil storage holes 46 and the annular oil groove 47 may be omitted or the oil supply groove 45 and the oil storage holes 46 and the annular oil may be omitted. It is also possible to omit groove 47. Also, when the first clutch plate 12 is engaged with the side gear 11, the shape or dimension of one spline gear 34a is different from that of the other spline gear 34a so that the oil supply groove 45 is properly disposed at a position corresponding to the oil reservoir 43. By setting, the first clutch plate 12 cannot be coupled to the side gear 11 unless the oil supply groove 45 is in the circumferential position corresponding to the oil reservoir 43.

Referring to the operation of the lubricating oil supply means 40, the lubricating oil is filled up to about 1/3 of the height in the differential gear case 13, and the entire pinion gear 15 revolves to the lower side and the lower side of the side gear 11. Is configured to soak in lubricating oil. For this reason, the lubricating oil in the differential gear case engaged with the engagement portion of the side gear 11 and the pinion gear 15 is transferred from the engagement portion of the side gear 11 and the pinion gear 15 to the main connection by the pumping action of the engagement of both gears 11 and 15. To the oil reservoir 43 formed at the spline shaft portion 34 of the side gear 11 and the coupling portion 17 of the clutch plates 12 and 14 through the radial connection passage 44 by centrifugal force by the rotation of the side gear 11 from the main connection passage 41. do. The lubricating oil of the oil storage part 43 is transferred from the oil storage part 43 to the outer circumferential side along the oil supply groove 45 by the centrifugal force of the clutch plates 12, 14, and is also supplied to the oil storage hole 46 and the annular oil groove 47, and thus the second clutch plate. The occurrence of friction noises between the clutch plates 12 and 14 when the sliding surfaces 12a and 14a of the 14 and the first clutch plate 12 are lubricated and differentiald within the initial torque are prevented. In addition, the lubricating oil in the oil reservoir 43 is supplied between the side gear 11 and the side wall of the differential gear case 13 through the guide groove 42 from the end of the side wall of the differential gear case 13 in the main connection path 41 so as to be differential from the side gear 11. Since it is also supplied to the sliding part with the gear case 13, seizure (sticking) of the side gear 11 and the differential gear case 13 is prevented.

In the differential device 10 shown in FIG. 1, the inner diameter of the pressure ring 18 is set larger than the outer diameters of the gear portion 28 and the spline shaft portion 34 of the side gear 11, and the outer diameters of the gear portion 28 and the spline shaft portion 34 are set substantially the same. The spline shaft 34 is formed in the outer circumference of the side gear 11 over its entire length, and the pressure ring 18 is formed in a thin thickness in the axle direction so that the number of clutch plates 12 and 14 can be increased as much as possible so that the differential limiting function can be properly obtained. Consists of. For this reason, the spline shaft part 34 of the side gear 11 is thicker than before, and the main connection path 41 and the radial connection path 44 can be formed effectively using the dead space of the spline shaft part 34. FIG.

Further, in the differential device 10, both pressure rings 18 are pressed in the direction approaching each other by the pressing means 21 without passing through the clutch means 16, so that the timing of switching from the differential state to the differential limit state is the operating force F of the operating means 22. And the pressurization means of the pressurizing means 21, and by setting the pressurization means of the pressurizing means 21 properly, the differential state is reliably obtained when turning at low speed, and the differential limiting reliably when turning at high speed and high load. Although it is configured so that the state can be obtained, the pressure contact between the clutch plates 12 and 14 is made only with the disc spring 33 provided for the purpose of eliminating the play, and since the pressure means 21 does not press, the occurrence of friction noise is also reduced by the above configuration. .

The omission of the main connection path 41 and the radial connection path 44 is also a category of the present invention. In this case, in the oil storage part 43 into the oil storage part 43 from the end of the side wall side of the differential gear case 13 in the oil storage part 43. Lubricant oil enters, and the lubricating oil is transferred to the oil supply groove 45 by the centrifugal force of the side gear 11 and the clutch plates 12, 14.

The lubricant supply means 40 of the present invention can also be applied to the differential device 100 of the background art shown in FIG. In the meantime, the same members as those of the differential apparatus 100 described in the background art are denoted by the same reference numerals, and detailed description thereof will be omitted.

As shown in Fig. 7, the lubricating oil supply means 50 of the differential apparatus 100A will be described. The oil extending in the axial direction to the spline shaft portion 52 in the side gear 51 and the engaging portion 55 of the first clutch plate 54 in the clutch means 53. The storage section 56 is formed at regular intervals in the circumferential direction, one end of the oil storage section 56 is connected in the differential gear case 101, and the other end is connected to the through hole 57 formed in the bottom of the side gear 51.

The oil reservoir 56 is formed with a groove in which one spline groove 52a of the spline shaft 52 is deeper than another groove. It is also possible to form by missing all or the radially outer end of one spline gear, or it can also be formed by missing all or the inner circumference of one row of pole portions arranged in the axial direction of the first clutch plate 54.

Although not shown in the drawing, the first clutch plate 54 and the second clutch plate 58 are provided with an oil supply groove 45, an oil storage hole 46 and an annular oil groove 47, as in the clutch plates 12 and 14 of the embodiment.

In the lubricating oil supply means 50, the lubricating oil is transferred from the engaging portion of the side gear 51 and the pinion gear 105 to the oil storage portion 56 through the through hole 57 by the pumping action at the time of the engagement of the side gear 51 and the pinion gear 105. As in the above embodiment, the lubricating oil is supplied between the sliding surfaces of the clutch plates 54 and 58 via the oil supply groove 45, the oil storage hole 46, and the annular oil groove 47, and the sliding surface is lubricated, whereby the clutch at the time of differential within the initial torque Friction of the plates 54 and 58 is prevented.

The differential apparatus according to the present invention can supply lubricating oil between the coupling portion of the side gear and the clutch plate between both clutch plates by using the pumping action in the coupling portion of the side gear and the pinion gear, the centrifugal force caused by the rotation of the side gear, and the like. Therefore, lubricant oil can be transferred between both clutch plates without increasing the number of parts or complicating the configuration of the differential device, and it is possible to effectively prevent the occurrence of friction noise of the clutch plate when differential is achieved within the initial torque. .

Claims (10)

A differential device comprising a clutch means having a first clutch plate integrally rotating with a side gear and a second clutch plate integrally rotating with a differential gear case, Lubricating oil supply means for supplying lubricating oil in the differential gear case is provided between the side gear and the clutch plate sliding portion between the sliding surfaces of both clutch plates. Differential device, characterized in that. The method of claim 1, As the lubricating oil supply means, a connection path is formed in the side gear, which connects the base of the side gear and the coupling portion of the side gear and the clutch plate. Differential device, characterized in that. The method of claim 2, An oil reservoir is formed at a coupling portion of the side gear and the clutch plate, and a connection path is connected to the oil reservoir. Differential device, characterized in that. The method of claim 3, The oil storage part is formed in the differential gear case at the end part on the opposite side to the gear part of the side gear. Differential device, characterized in that. The method of claim 1, As the lubricating oil supply means, an oil storage portion is formed at the engaging portion of the side gear and the clutch plate, and the end of the oil storage portion is connected in the differential gear case on the side opposite to the gear portion of the side gear. Differential device, characterized in that. The method according to any one of claims 3 to 5, At least one coupling portion of the side gear and the first clutch plate is omitted to form an oil reservoir. Differential device, characterized in that. The method according to any one of claims 1 to 6, At least one of the first clutch plate and the second clutch plate is provided with an oil supply groove for supplying lubricating oil supplied to the engaging portion of the side gear and the clutch plate between the sliding surfaces of both clutch plates. Differential device, characterized in that. The method of claim 7, wherein At least one sliding surface of the first clutch plate and the outer clutch plate is provided with an annular oil groove connected to the oil supply groove. Differential device, characterized in that. The method according to claim 7 or 8, In at least one sliding surface of the first clutch plate and the second clutch plate, an oil storage hole for storing lubricating oil supplied from the oil supply groove is formed. Differential device, characterized in that. The method of claim 9, A plurality of the oil storage holes are formed at predetermined intervals in the circumferential direction of the clutch plate, and the radial position of the clutch plate in the adjacent oil storage holes is changed. Differential device, characterized in that

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